JP2023098971A - Lubricated sliding bearing with adjustment of property of lubricant in certain part of bearing gap - Google Patents

Abstract

To provide a bearing device which combines some of the advantages of hydrostatic and hydrodynamic bearing devices.SOLUTION: The invention relates to a bearing device 10 comprising: a first surface and a second surface which are moveable relative to one another, where the first and second surfaces are separated by a bearing gap 16 filled with a lubricant, which is a magnetorheological liquid or an electrorheological liquid or a lubricant having a temperature dependent viscosity, or a lubricant having a controllable slip velocity; one or more supply inlets 18 in the first or second surface; and an activator 20 embedded in the first or second surface and configured to locally increase a viscosity of the lubricant in an obstruction zone, thereby inhibiting a flow of the lubricant in the obstruction zone. The bearing gap comprises a non-obstruction zone 24 in which the flow of the lubricant is not inhibited. The obstruction zone 22 inhibits the lubricant from flowing out of the bearing gap. The lubricant having an increased viscosity acts as an obstruction of the flow path.SELECTED DRAWING: Figure 1A

Description

The present invention relates to a bearing device having an electrorheological or magnetorheological lubricant or a lubricant with a temperature dependent viscosity and provided with one or more active devices for locally increasing the viscosity of the lubricant. The present invention also provides a bearing device having a lubricant with slip velocity controllable using an electric field and comprising one or more (electro)active devices for locally reducing the slip velocity of the lubricant. Regarding.

There are many different bearing devices that use lubricants. These bearing devices are widely used in mechanical equipment, including ships, power plants, other vehicles such as automobiles, and other mechanical equipment.

Bearing devices can be classified as static (hydrostatic), hydrodynamic (hydrodynamic), or hybrid. Each of these has unique advantages and disadvantages. It should be noted that the term "bearing device" in the context of this specification is intended to be limited to bearing devices without roller elements, such as ball bearings. In other words, the load is transmitted by the lubricant between the fixed part of the bearing device and the moving part of the bearing device.

An advantage of hydrostatic bearing devices is that contact between the fixed and moving parts never occurs during use, regardless of whether the moving parts move. A drawback of hydrostatic bearing devices is that they require a continuous supply of lubricant by an external pressurized source. When the external pressurization source fails, the lubricant in the bearing loses pressure. The parts can come into contact and the bearings can be damaged or worn as a result.

A further drawback of hydrostatic bearing devices is that the surfaces at the ends of the bearing gap need to be spaced closer together in order to obtain and maintain higher static pressures for improved performance. is. This is commonly done using so-called "surface texturing" in the form of peaks and pads. This surface texturing requires very precise machining to achieve the desired surface finish. Furthermore, due to the need for very precise machining, surface texturing is also vulnerable to wear and tear when moving and stationary parts come into contact with each other.

An advantage of hydrodynamic bearing devices is that they do not require surface texturing. The surfaces of the fixed and moving parts can be perfectly smooth, and such surfaces are easy to manufacture. A further advantage is that the hydrodynamic bearing device does not require a pressurized source of lubricant. This reduces the risk of failure.

A drawback of hydrodynamic bearings is that their operation depends on the build-up of dynamic pressure. This pressure is formed only when the mobile part moves relative to the fixed part. If the moving part does not move or moves too slowly, physical contact between the moving part and the fixed part occurs, resulting in wear and tear of the parts. This especially occurs during machine start-up or deceleration when the relative speed of the parts is low. In other words, the hydrodynamic bearing must have sufficient speed for actuation.

Also note that hydrodynamic bearing devices typically have a supply of lubricant to prevent the bearing device from running out. However, for hydrodynamic bearing devices, the pressure at which the lubricant enters the bearing is very low and does not significantly contribute to the load bearing capacity of the hydrodynamic bearing. Instead, the load-bearing capacity is created by the dynamic pressure created by the rotation of the rotating part relative to the stationary part.

Hybrid bearings exist that combine some of the advantages of hydrostatic and hydrodynamic bearings. However, the performance of hybrid bearings is limited. Generally, hybrid bearings have limited surface texturing. A small amount of surface texturing improves performance in dynamic regimes, but limits performance in static regimes. Also, static actuation regimes require pumps, which are prone to failure.

Bearing devices can also be classified according to their shape and the motion they allow. Journal bearings typically surround the rotating shaft to provide radial support. Journal bearings are sometimes called radial bearings. Thrust bearings also surround the rotating shaft but provide axial support for the shaft. Thrust bearings are sometimes called axial bearings. A flat bearing has a flat bearing surface and provides support in a direction perpendicular to the flat bearing surface. A thrust bearing is an example of a flat bearing. Conical bearings also exist. Conical bearings form a hybrid between journal bearings and thrust bearings and can transmit both axial and radial loads. Often the conical bearings are provided in pairs, the first and second conical bearings being tapered in opposite directions.

It is a long-standing goal to improve lubricity in order to reduce wear and tear in various parts of bearing devices. In the past, bearing devices have been disclosed that use lubricants with electrorheological or magnetorheological properties. Electrorheological lubricants (ERLs) are lubricants comprising electropolarizable particles dispersed in a liquid. A magnetorheological lubricant (MRL) is a lubricant comprising magnetic particles dispersed in a fluid.

These bearing devices are equipped with an active device for increasing the viscosity of the lubricant in order to improve the lubricity of the bearing device.

One such disclosure is US Pat. This document discloses a hydrodynamic bearing device with an active device. This active device can be used to locally increase the viscosity of the lubricant. In this way, the lubricant can be manipulated to stay in specific areas, thereby improving lubricity and the load that the bearing device can carry.

Of particular interest is the embodiment disclosed in FIG. 14 of US Pat. FIG. 14 shows a hydrodynamic journal bearing device. The active devices 200, 2001 are elongated and extend parallel to the main axis of the shaft. The active device extends from one bearing end to the opposite bearing end. The active devices are circumferentially spaced about the shaft. The active device increases the viscosity of the lubricant in the closed area within the bearing gap near the active device. As the rotating shaft rotates, it forces the lubricant to flow in the same direction as the direction of rotation of the shaft. Lubricant with increased viscosity at each blocked area in each active device in the bearing gap prevents the lubricant from crossing each blocked area. As a result, the lubricant pressure in the bearing gap is increased immediately upstream of each active device. This improves the dynamic pressure effect of the bearing.

A disadvantage of the embodiment of FIG. 14 is that there is no or a relatively small increase in pressure for regions within the gap that are far from and unaffected by the active device. The combined effect of the active device is limited because the active device only acts on a portion of the total bearing surface.

A solution proposed in US Pat. No. 5,900,003 is to provide a large number of active devices to cover the entire inner surface of the fixed part, see column 20, lines 31-41. However, the present invention recognizes that this solution is rather complex and expensive.

The present invention is based on the insight that a limited number of active devices can be used to extend the effect over the entire bearing gap or most of the bearing gap.

Another publication in this field is Non-Patent Document 1. Non-Patent Document 1, referring to FIGS. 1 and 3, discloses a hydrostatic bearing device with ridges and pads. A hydrostatic bearing device comprises an inlet and an external pressure source. An active device in the form of a coil is provided for locally increasing the viscosity of the lubricant. The coil extends around the bearing and can be seen in FIG. A drawback of this bearing device is that very precise machining is still required to make the ridges and pads. Weaknesses associated with ridge and pad wear and tear still exist.

A further improvement to the same idea is disclosed in Non-Patent Document 2. The device disclosed in Non-Patent Document 2 also requires precision machining and is more fragile.

U.S. Pat. No. 7,980,765

Hesselbach, "Active hydrostatic bearing with magnetorheological fluid", Journal of applied physics, May 15, 2003, Vol. 93, p. 8441-8443 Guldbakke and Hesselbach, "Development of bearings and a damper based on magnetically controllable fluids," IOP Publishing, Sept. 8, 2006, Vol. 38, No. 18

It is an object of the present invention to develop many of the advantages of hydrostatic and hydrodynamic bearing devices, in particular hydrostatic bearings in which contact between fixed and moving parts is avoided both during movement and at rest of the various parts. It is an object of the present invention to provide a bearing device that combines the advantages of the device with those of hydrodynamic bearing devices, in particular the absence of surface texturing. The lack of surface texturing has the associated advantage of reduced brittleness.

It is an object of the present invention to provide a bearing device capable of carrying greater loads than prior art bearing devices using electrorheological or magnetorheological lubricants. The present invention may be used with lubricants that have temperature dependent viscosities or controllable slip rates.

A further object of the present invention is to provide an improved hydrodynamic bearing.

It is a further object of the present invention to provide an improved hydrodynamic bearing having reduced leakage of lubricant from the bearing gap compared to prior art hydrodynamic bearing devices.

A further object of the present invention is to provide a bearing device that replaces the prior art.

To achieve at least one of these objectives, the present invention provides:
- a first surface and a second surface movable relative to each other and facing each other, the first surface and the second surface being separated by a bearing gap filled with lubricant; a first surface and a second surface, wherein the lubricant is a magnetorheological or electrorheological liquid, a lubricant with a temperature dependent viscosity, or a lubricant with a controllable slip velocity;
- one or more feed inlets in the first or second surface, the feed inlets being configured to feed lubricant from a pressurized liquid supply to the bearing gap;
- one or more active devices embedded in the first surface or the second surface for locally increasing the viscosity of the lubricant or the slip velocity of the lubricant in at least one blockage area in the bearing gap; one or more active devices configured to locally reduce , thereby locally blocking lubricant flow through the bearing gap in the blockage region;
with
the bearing gap comprises at least one non-obstructed area through which lubricant flow is unimpeded, the non-obstructed area surrounding the associated feed inlet;
A lubricant flow path is defined through the bearing gap, the flow path originating at the at least one feed inlet, extending along the at least one non-obstructed area, across the occluded area, and through the bearing gap. terminating at the ends,
the first and second surfaces are smooth and continuous, especially free of surface texturing in the form of ridges and pads, without abrupt changes in bearing gap height;
at least one occlusive region, by itself or in cooperation with other occlusive regions, surrounds at least one non-occluded region;
Lubricants with increased viscosity or reduced slip velocity in the clogged area acted as flow path blockages and had increased viscosity or reduced slip velocity on their own or in other clogged areas. cooperates with the lubricant to prevent the lubricant from flowing out of the non-blocking area and out of the bearing gap through the bearing gap end, thereby reducing the pressure of the lubricant in the non-blocking area; to a level sufficient to carry the load on the bearing device and at the same time prevent contact between the first and second surfaces.

When the active device is activated, the obstruction in the obstructed area prevents lubricant from flowing through the obstructed area and increases the pressure in the non-occluded area compared to the non-activated state of the active device. .

In effect, the occluded area acts as a pad (also called surface texturing) of the hydrostatic bearing device and replaces the pad of the hydrostatic bearing device. This has the advantage that the benefits of hydrodynamic bearing devices can be realized without peak and pad configurations, in other words without surface texturing. Accordingly, a bearing device according to the present invention has smooth and continuous first and second surfaces without abrupt changes in the surfaces.

Thus, an appropriately chosen pattern of active devices creates a "virtual" surface texture. An electrostatic, magnetic, or temperature field with a particular distribution will produce a particular spatial viscosity change in the fluid. This spatial viscosity variation forces the fluid to flow in a pattern similar to that observed for fluids of constant viscosity flowing in bearings with physical surface textures.

Additionally, this virtual texture may appear, disappear, or be altered to define different virtual textures, allowing the bearing to function at optimum efficiency over a wide range of operating conditions. .

Bearing performance is affected by the selection of active devices that are operated and the extent to which these active devices are operated. This selection and degree of activation allows for optimal bearing operation for different operating conditions, such as different sliding directions or different loads.

A bearing device according to the invention may be used with a lubricant having a controllable slip velocity. This may be a lubricant with an electric dipole. Activation of the (typically electrical) active device has the effect that the dipoles are oriented within the occlusion region. This has the effect that the slip velocity is reduced locally, i.e. at the occlusion areas, and as a result the lubricant molecules tend to adhere better to the first and second surfaces. have. This increases the slip angle of the lubricant on the bearing surface in the blocked area and impedes the flow of lubricant in the blocked area.

Theoretically, fluid mechanics generally assumes no-slip boundary conditions at the interface. In practice, however, the boundary conditions may not always apply perfectly when the slip velocity of the lubricant is high. In the present invention, the boundary condition, also called slip angle, can be influenced by changing the slip velocity of the lubricant. Since in practice the bearing gap is very thin (tens of micrometers), the effect of increasing the slip angle is to impede the flow in the blockage area.

A dipole may have a positively charged side and a negatively charged side. One of these sides may be attracted to the interface and the other side may be repelled by the interface. These dipoles may attach to the interface if the active device orients the dipoles so that the side that is attracted to the interface faces the interface. In this way the slip angle may be increased and the zero velocity boundary condition may be fully realized. Boundary conditions may be locally modified without changing the viscosity of the lubricant. It is therefore a different way to achieve the same result than using an electrorheological or magnetorheological lubricant or a lubricant with a temperature dependent viscosity according to the present invention.

Lubricant is trapped in the non-occluded area because the non-occluded area is completely surrounded by the occluded area. The occluded area acts as an occluder. Those skilled in the art will appreciate that this confinement is not absolute in practice and that some lubricant will continue to pass through the closed area to reach the bearing gap ends. However, in practice it is not the main issue.

Those skilled in the art will also understand that in at least one non-occluded region where one or more active devices have no effect, the term "ineffective" means that the magnetic field of the electric field theoretically has no end but gradually increases in strength. You will understand that it should be interpreted according to the laws of physics that determine the fall. The term "no effect" means that the effect of the occluded area on viscosity is negligible.

The pressure of the lubricant within the non-occluded region is increased to a level sufficient to carry the load on the bearing device and prevent contact between the first and second surfaces. It should be appreciated that the lubricant in the closed area is also under pressure and carries some of the load to help prevent contact between the first and second surfaces.

In one embodiment of the bearing device, the active device is an electromagnet or permanent magnet that creates a magnetic field, or an electroactive device that can be charged to create an electric field. In alternative embodiments, the active device may be a cooling element configured to cool the lubricant within the at least one occlusion region.

In one embodiment, the bearing device comprises a plurality of non-occluded areas, in particular three non-occluded areas, each non-occluded area having a respective inlet, and a plurality of occluded areas, each occluded area a plurality of occlusive regions surrounding an associated non-occluded region to prevent lubricant from escaping from the associated non-occluded region.

In one embodiment of the bearing device, the non-occluded area is pie-shaped, circular, square, rectangular, triangular, polygonal or elliptical, or more generally any shape that can be enclosed by the occluded area. In the case of polygons, the non-occluded areas may be hexagons. Other shapes may be used, and combinations of different shapes may be used.

In one embodiment of the bearing device, the first surface and the second surface are cylindrical or conical, spherical or flat and extend about the main axis of rotation.

In one embodiment of the bearing device, the first and second surfaces are cylindrical, conical, spherical or flat, and the bearing device comprises a plurality of non-occluded areas, each non-occluded area being an occluded area. and each occluded region has a first axial portion and a second axial portion extending a predetermined axial distance and a first circumferential portion extending a predetermined circumferential distance. a directional portion and a second circumferential portion, each closure region having four corners interconnecting the first and second axial portions and the first and second circumferential portions; Prepare.

In one embodiment, the bearing device comprises at least a ring-shaped first closure region and a ring-shaped second closure region, the first closure region being cylindrical, conical, spherical or Disposed at a first end of the flat bearing and a second occlusion region is disposed at a second opposite end of the cylindrical, conical, spherical or flat bearing and is non-occluded. A region is provided between a first occlusion region and a second occlusion region, the first and second occlusion regions extending from the non-occlusion region and through the bearing gap end into a cylindrical, conical shape. Acts as a seal to prevent lubricant from escaping from shaped, spherical or flat bearing gaps.

In one embodiment of the bearing device, the first and second surfaces are cylindrical, conical, spherical or a combination of flat surface sections.

In one embodiment, the bearing device comprises at least one outer occlusive region surrounding an inner occlusive region. This makes the overall configuration more stable.

In one embodiment, the bearing device is a thrust bearing configured to carry the load in the axial direction, the first and second surfaces being annular and extending about the main axis of rotation of the bearing device. , the primary axis of rotation extends orthogonally to the first surface and the second surface, the bearing device has an outer peripheral bearing end and an inner peripheral bearing end, the bearing device having at least one non-axial bearing end; At least one outer blockage region for blocking lubricant flow from the blocking region to the outer peripheral bearing end and at least one inner blockage for blocking lubricant flow from the at least one non-blocking region to the inner peripheral bearing end. and at least one non-occluded region (24) is located between the inner occlusive region and the outer occlusive region.

In one embodiment of the bearing device, the first surface and the second surface are flat or spherical and the bearing device comprises an outer bearing gap end and a lubricant flowing through the outer bearing gap end into the bearing gap. It comprises only a non-occluded area surrounded by an annular occluded area that prevents outflow from.

In one embodiment of the bearing device, the one or more active devices are referred to as primary active devices, and the bearing device further includes one or more reactive devices (which are electromagnets or permanent magnets or electroactive devices or heating elements). anti-activators), wherein the counter-activator device creates a reverse magnetic or electric field to counteract the magnetic or electric field produced by the primary active device in at least a portion of the non-occluded region, or the non-occluded region or A heating element for heating the lubricant in at least a portion of the non-occluded region. In alternative embodiments, the reaction device may comprise a heating element.

In one embodiment of the bearing device, the counter-actuation device acts on a portion of the non-occlusion zone, which is referred to as the anti-obstruction zone, the non-occlusion region being the primary active device. or further comprising a non-affected area not under the influence of the counteractive device, wherein at least one anti-occlusion area is positioned adjacent to the occlusion area and between the occlusion area and the non-affected area.

In one embodiment of the bearing device, the active device is an electromagnet and the bearing device further comprises at least one passive ferromagnetic member configured to increase the electromagnetic field.

In one embodiment of the bearing device, the electromagnetically active device is a coil having a primary axis, the coil being positioned below the first or second surface and the ends of the coil having the coil positioned thereunder. the at least one ferromagnetic member having an inner member disposed within the coil and an outer member disposed outside the coil; has respective inner and outer projections extending beyond the ends of the coil toward said first or second surface, with an aperture between said inner and outer projections.

In one embodiment of the bearing device, the bearing device does not include roller elements such as ball or cylindrical roller elements.

In one embodiment of the bearing device, one or more active devices are positioned below a layer of material covering at least one active device to form the first or second surface.

In one embodiment of the bearing device, the occlusion area is defined by a plurality of active devices arranged adjacent to each other along a predetermined line. This line may be curved in one or two planes of curvature and/or may have angles.

In one embodiment of the bearing device, the bearing gap has a uniform height between the entrance and the end of the bearing gap.

Hydrodynamic Bearing Device In a further embodiment, the present invention relates to a hydrodynamic bearing device,
- a first bearing surface;
- a second bearing surface facing the first bearing surface;
and
the first and second bearing surfaces are configured to rotate relative to each other about a primary axis of rotation;
- a bearing gap defined between a first bearing surface and a second bearing surface, the first and second bearing surfaces being smooth and free of surface texturing, the bearing gap comprising: The bearing gap is filled with a lubricant, the lubricant can be a magnetorheological or electrorheological liquid, a lubricant with a temperature dependent viscosity, or a lubricant with a controllable slip velocity is the bearing gap, and
- A plurality of active devices embedded in the first or second bearing surface, the plurality of active devices locally increasing the viscosity of the lubricant or increasing the slip velocity of the lubricant within the plurality of occlusion regions. a plurality of active devices configured to reduce the , thereby inhibiting lubricant flow through the bearing gap at each blockage region;
- a plurality of unobstructed areas in which the flow of lubricant is unobstructed, alternating in the direction of relative movement between the first and second bearing surfaces, the blocked areas and the unobstructed areas, each a plurality of non-occluded regions, the non-occluded regions positioned upstream of the associated occlusive region;
and
Each occluded region has a curved or angled shape, the curved or angled shape defines a downstream oriented apex, and the occlusive region comprises first and second Located upstream of each blockage area by locally increasing viscosity or reducing slip velocity in the blockage area to prevent lubricant flow across each blockage area when the surfaces move relative to each other are configured to cause a local increase in lubricant pressure in the bearing gap in the non-obstructed regions, and particularly in the peak regions located immediately upstream of each crest.

The closed area functions as surface texturing in hydrodynamic bearings. Generally, such surface texturing of prior art hydrodynamic bearings is provided in the form of grooves. In the prior art, such grooves may have convoluted shapes designed to optimize dynamic pressure build-up. Grooves require precision machining and are vulnerable to wear and tear. The absence of these grooves advantageously makes the bearing easier to manufacture and less brittle. As a result, the service life of the bearing device can be longer.

In one embodiment of the hydrodynamic bearing device, each closed region comprises left and right sections extending at an angle to the radial direction, the left and right sections directing lubricant to the peak region. Orient towards.

In one embodiment of the hydrodynamic bearing device each apex is arranged in a central region of the first or second surface, the apex being in particular a predetermined distance from the inner bearing end of the first or second surface. Located at a distance, the distance being 40 to 60 percent of the width of the first or second surface. The distance to the outer bearing edge may also be 40 to 60 percent of the width of the first or second surface.

In one embodiment, the hydrodynamic bearing device is a thrust bearing device, the first and second surfaces are flat and extend perpendicular to the main axis of rotation, and the closed area has a predetermined radius Extends over a directional distance.

In one embodiment of the hydrodynamic bearing device, the first and second surfaces are annular and the bearing gap is annular.

In one embodiment of the hydrodynamic bearing device, the closed area has a V-shape or a U-shape.

In one embodiment of the hydrodynamic bearing device, the bearing is a journal bearing or a conical bearing and the curved or angular closed areas are spaced around the circumference of the first or second surface and have predetermined extends for an axial distance of

Note that there is a special class of hydrodynamic bearings commonly referred to as tilt pad bearings. In this embodiment the bearing device is a tilt pad bearing device and comprises a plurality of tilt pads tiltable about a pivot axis, the first surface comprising a plurality of first surface sections, each first a surface section associated with a tilt pad, a bearing gap comprising a plurality of bearing gap sections, each bearing gap section associated with a tilt pad,
Each first surface section is smooth and free of surface texturing, and each individual bearing gap section between the tilt pad and the opposite second surface is free of abrupt changes in bearing gap height. without
Each first surface section comprises an occlusion area having a curved or angled shape, the curved or angled shape defining a downstream oriented apex, the occlusion area comprising: Locally increasing the viscosity or locally reducing the slip velocity in the blockage area to prevent lubricant flow across each blockage area when the first and second surfaces move relative to each other. is configured to cause a local increase in the pressure of the lubricant in the bearing gap in the non-occluded region located upstream of each clogged region, and particularly in the peak region located immediately upstream of each crest by there is

Between the tilt pads are not considered part of the bearing gap and part of the first surface because they do not substantially contribute to the transmission of force between the first surface and the second surface. Note that there may be non-supporting areas that are not considered parts.

The shape of the occluded area of each tilt pad is generally U-shaped, but may also have an angled configuration such as a V-shape, or may have a curved configuration. Also, a single tilt pad may be provided with a plurality of occlusion areas side by side.

The invention further relates to a hydrodynamic journal bearing device,
- a cylindrical bearing member extending around the shaft, the cylindrical bearing member comprising a first surface facing inward;
- a shaft with a second surface facing outward;
and
a hydrodynamic journal bearing device having a predetermined bearing length and having a first end and an opposite second end;
- a bearing gap present between the first surface and the second surface, the bearing gap comprising a first bearing gap end at the first bearing end and a second bearing gap end at the second bearing end; two bearing gap ends, the first bearing surface and the second bearing surface being smooth and continuous, the bearing gap being filled with a lubricant, the lubricant being , a magneto-rheological or electro-rheological liquid, a lubricant with a temperature dependent viscosity, or a lubricant with a controllable slip velocity, a bearing gap;
- at least a first active device and a second active device embedded in the first or second surface to localize the viscosity of the lubricant within the first and second closed areas in the bearing gap; is configured to either locally increase or locally reduce the slip rate of the lubricant, and when the first active device and the second active device are activated, the first active device and the second active device The active device increases the viscosity of the lubricant within the first and second regions of occlusion or decreases the slip velocity of the lubricant to prevent the lubricant from flowing across the first and second regions of occlusion. a first active device and a second active device that block;
and
the first surface and the second surface are smooth and continuous without surface texturing and without abrupt changes in bearing gap height;
the bearing gap has at least one unobstructed area through which lubricant flow is unimpeded;
the first and second bearing gap ends are annular, extend about the shaft and extend in a plane orthogonal to the longitudinal bearing axis;
The first and second occlusion areas are ring-shaped and located at opposite ends of the journal bearing, and the non-occlusion area is located between the first occlusion area and the second occlusion area. ,
The first blockage area prevents lubricant from reaching the first bearing gap end, the second blockage area blocks lubricant from reaching the second bearing gap end, and
Together, the first blocked area and the second blocked area prevent lubricant from flowing out of the unblocked area and out of the bearing gap through the end of the bearing gap.

This embodiment of the invention provides a very simple overall structure for a hydrodynamic journal bearing device. Lubricant is effectively prevented from flowing out of the end of the bearing gap.

In one embodiment of the hydrodynamic journal bearing device, the height of the bearing gap is constant in the axial direction.

In one embodiment of the hydrodynamic journal bearing device, the height of the bearing gap varies in the circumferential direction. This is customary for hydrodynamic journal bearings, as the shaft is typically slightly off-center to create the necessary radial force.

In one embodiment of the hydrodynamic journal bearing device, the bearing device has a length and each closed area has a width, the width of each closed area being 10 percent of its length. is less than Advantageously, most of the bearing device contributes to carrying the load.

The invention further relates to a drive assembly comprising a shaft, said shaft being supported by at least one bearing device according to the invention.

In one embodiment of the drive assembly, the shaft comprises a first bearing device according to the invention as far as the journal bearing device is concerned, a second bearing device according to the invention as far as the journal bearing device is concerned and a thrust bearing device as far as the journal bearing device is concerned. and a third bearing device according to the invention in the first and second journal bearing devices for positioning and supporting the shaft in two independent radial directions (Y, Z). , a third thrust bearing device to position and provide support for the shaft in the axial direction (X). This configuration provides support for the shaft in all required directions.

The invention further relates to a watercraft comprising a hull, an engine, a propeller and a drive assembly according to the invention connecting the engine to the propeller. The invention has been found to be particularly suitable for marine vessels as it provides a robust and reliable overall construction. It should be noted that the present invention may be used in all types of equipment including other vehicles, power plants, wind turbines, engines in general and other types of equipment.

These and other aspects of the present invention will be better understood by reference to the following detailed description and explained in connection with the accompanying drawings, in which like reference numerals indicate like parts, so that can be easily recognized.

1 is an isometric view of a first embodiment of the invention; FIG. FIG. 1B illustrates the pressure gradient in the embodiment of FIG. 1A; Figure 4 is an isometric view of a second embodiment of the invention; Figure 3 is an isometric view of a third embodiment according to the present invention; Figure 4 is a side view of the embodiment of Figure 3; Figure 5 is an isometric view from below of a variant of the embodiment of Figures 3 and 4; Figure 6 is an isometric view from above of the embodiment of Figure 5; Figure 7 is a side view of the embodiment of Figures 5 and 6; Figure 3 is an isometric view of another embodiment of the present invention; Figure 3 is an isometric view of another embodiment of the present invention; Figure 3 is an isometric view of another embodiment of the present invention; Figure 3 is an isometric view of another embodiment of the present invention; Figure 3 is an isometric view of another embodiment of the present invention; Figure 3 is an isometric view of another embodiment of the present invention; Figure 4 is an isometric view of yet another embodiment of the present invention; 1 is an isometric view of a drive assembly having three bearing devices according to the invention; FIG. 1 is an isometric view of a marine vessel with a drive assembly having three bearing devices according to the invention; FIG. 1 is a top view of a linear bearing device according to the invention; FIG. 1 is a top view of a planar bearing device according to the invention; FIG. FIG. 4 is a side cross-sectional view of another embodiment of the invention; Figure 17 is an isometric view of the embodiment of Figure 16; Figure 3 is an isometric view of another embodiment of the present invention; FIG. 19 is a top view of the embodiment of FIG. 18; Figure 19 is a side cross-sectional view of the embodiment of Figure 18; FIG. 4 is an isometric view of an embodiment of the invention comprising a tilt pad; Figure 22 is a top view of the embodiment of Figure 21; Figure 22 is a side cross-sectional view of the embodiment of Figure 21;

Referring to FIG. 1, a first embodiment of the invention is shown. A bearing device 10 is provided. The bearing device comprises a first surface 12 and a second surface 14 movable relative to each other. In this embodiment both the first and second surfaces are flat. The first surface and the second surface face each other. The first and second surfaces are separated by a bearing gap 16 that is filled with lubricant. The bearing gap may have a height as high as tens of micrometers, but obviously other heights can be used depending on the size of the bearing device. First surface 12 is formed by first member 13 and second surface 14 is formed by second member 15 .

Lubricants are liquids. The lubricant is a magnetorheological or electrorheological liquid, or a lubricant with a temperature dependent viscosity, or a lubricant with a controllable slip velocity.

The bearing device comprises one or more feed inlets 18 on either the first surface or the second surface. In this embodiment the feed inlet is provided on the first surface 12, but it may be envisaged that the inlet is provided on the second surface. Each supply inlet 18 is configured to supply lubricant to the bearing gap from a pressurized liquid supply. A pressurized liquid supply is provided in the case of hydrostatic bearing devices, but is not considered part of the present invention.

The bearing device includes one or more active devices 20 embedded in the first surface 12 and locally increasing the viscosity of the lubricant in at least one closed region 22 within the bearing gap. It is configured to increase, thereby preventing the flow of lubricant through the bearing gap in the blockage area. The bearing gap comprises an unobstructed area 24 through which lubricant flow is unobstructed. The non-occluded area 24 comprises a neutral lubricant having a lower viscosity. An unobstructed area 24 surrounds the feed inlet 18 . In this embodiment, the non-obstructing area 24 has a circular shape.

The occluded area may be defined by multiple active devices positioned adjacent to each other along a predetermined line. Each active device 20 , and likewise each occlusion region 24 , comprises two radially extending radial portions 29 A, 29 B and a circumferentially extending circumferential section 33 . An outflow region 35 is defined between each pair of radial portions 29 of adjacent occluded regions.

A lubricant flow path is defined through the bearing gap. The flow path originates at at least one feed inlet 18, extends along at least one non-occluded region 24, traverses the clogged region 22, and terminates at a bearing gap end 26. As shown in FIG.

In contrast to conventional hydrostatic bearing devices, first surface 12 and second surface 14 are smooth and continuous, free of surface texturing in the form of ridges and pads, and the height of the bearing gap without abrupt changes in The top surface of active device 20 is made flush with the rest of first surface 12 . This makes the bearing device relatively simple to manufacture and relatively robust.

The closed area 22 surrounds at least one non-closed area 26 and lubricant flows over the closed area 22 to the bearing gap end 26 and out of the bearing gap through the bearing gap end 26 . thereby preventing it from exiting the unoccluded area 26 .

Referring to FIG. 1B, this enclosure allows an external pressure source to apply pressure between the first and second bearing surfaces with the bearing device carrying the load without conventional surface texturing. It is possible to raise to a level that can prevent contact with In other words, the occlusive regions act as surface texturing, and in particular as pads. In FIG. 1B, channels 25 are indicated by arrows within the bearing gap. The pressure as a function p(x) of the distance x traveled along the channel is shown by the dashed line. In the non-occluded region 24, the pressure gradient p'(x) is relatively small. In the closed region, the pressure gradient p'(x) changes abruptly and the pressure drops to zero at the bearing gap end 26 .

Bearing gap end 26 is circumferential and extends around bearing gap 16 . In this embodiment, the bearing device comprises only an outer bearing gap end 26 and an unobstructed area 24 which prevents lubricant from escaping from the bearing gap through the outer bearing gap end. It is surrounded by a blocking annular closure area 22 . As described with reference to other embodiments, the bearing device may have multiple bearing gap ends.

The lubricant with increased viscosity in the occlusion areas 22 acts as a flow path blockage and by itself or in cooperation with other viscosity-increased lubricants in the occlusion areas causes the lubricant to at least One non-occluded area 26 is prevented from exiting, thereby reducing the pressure of the lubricant in the non-occluded area, which carries the load on the bearing device and prevents contact between the first and second surfaces. to a level sufficient to prevent

The active device may comprise an electromagnet or permanent magnet that produces a magnetic field. In another embodiment, the active device may comprise an electro-active device chargeable to create an electric field. In another embodiment, the active device is a cooling element configured to cool the lubricant within the at least one occluded region 22 . In another embodiment for use with lubricants having controllable slip rates, the active device is an electro-active device that creates an electric field, thereby orienting dipoles in the lubricant to increase the slip rate of the lubricant. to control.

Referring to FIG. 2, a similar embodiment is shown in which the active devices are disposed under a layer 28 of material covering at least one active device and forming the first surface or the second surface. be. This facilitates perfect smoothness of the first and second surfaces.

Although in the embodiment shown in FIGS. 1 and 2 the first and second surfaces are flat, in other embodiments the first and second surfaces may be spherical or spherical such as hemispherical. It may have some shape. At this time, the bearing gap also becomes spherical or hemispherical. The bearing device may be a swing arm bearing having first and second surfaces having the form of a "slice" of a sphere.

The bearing devices of Figures 1 and 2 allow movement of the first surface relative to the second surface in two independent directions of movement X, Y while providing support in a third direction of movement. The embodiment of Figures 1 and 2 also allows rotation of the first surface relative to the second surface about the Z-axis. 1 and 2 prevent rotation about the X and Y axes.

The bearing device may be devoid of roller elements, such as ball or cylindrical roller elements.

Referring to Figures 3 and 4, another embodiment is shown. The first and second surfaces 12, 14 are flat. The first and second surfaces are circular. The bearing device comprises a plurality of unobstructed areas 24A, 24B, 24C (commonly designated 24), in particular three unobstructed areas. Each unobstructed area has a respective inlet 18 . The bearing device comprises a plurality of occlusive regions 22A, 22B, 22C (commonly designated 22). Each occlusive region surrounds and inhibits lubricant from escaping the associated non-occluded region.

The unoccluded area in the embodiment of Figures 3 and 4 is pie-shaped (ie, in the shape of an arc). It should also be realized that the non-occluded areas may have different shapes, such as circular, square, rectangular, triangular, polygonal (eg hexagonal), elliptical, or combinations of these shapes.

These occlusion areas are spaced at regular angular intervals around the center 31 and/or around the central axis 30, in particular angular intervals of about 120 degrees.

The embodiments of FIGS. 3 and 4 provide the same motion and support capabilities as the embodiments of FIGS. 1 and 2, but the embodiments of FIGS. It differs in that it can provide better support for tilting of the second surface with respect to the surface. Therefore, it is better suited to maintain the orientation of the second surface with respect to the X and Y axes. The background to this is that the bearing gap is partitioned into three independent pressure zones, non-blocking zones 24A, 24B, 24C.

The pressure source may be configured to provide independent pressures to different non-occluded regions. A control unit 101 may be provided to control the different pressures. A sensor 102 may also be provided. The sensors may include pressure sensors for different non-occluded areas. The sensor 102 may be positioned within or at the entrance opening 18 . If there is a pressure differential, the control unit 101 may increase flow to one of the inlet openings 18 to restore pressure equilibrium. A position or orientation sensor may also be provided. If the second surface tilts, the tilt may be sensed by the sensor and an increase in pressure in one or more of the non-occluded areas may be effected by the control unit 101, resulting in a reversal of the tilt. and realignment of the first surface and the second surface occurs.

The bearing device allows movement in two independent directions X, Y and may provide support in a third direction Z. The bearing device may allow rotation about the Z axis and prevent rotation about the X and Y axes.

Those skilled in the art will appreciate that this embodiment may be extended and include multiple non-occluded regions surrounded by occluded regions. 3 and 4 have a circular shape, it is also possible to have different overall shapes such as square or rectangular shapes or rectilinear shapes. The bearing device is of considerable size and may have three or more non-obstructing regions.

Referring to Figure 14, a variant is shown in which the bearing device is a linear bearing device. The non-occluded regions 24A, 24B, 24C, 24D, etc. are arranged in a linear configuration, for example along the X axis, and allow movement of the second surface relative to the first surface along the X axis only, while the Z Support the second surface in the direction and via another means such as a guide surface in the Y direction. The different non-occluded regions 24 also provide support for tilting of the second surface relative to the first surface about the Y-axis and may also provide support for tilting about the X-axis. Another guide may provide support for rotation about the Z-axis.

The non-obstructing area 24 has a square or rectangular shape, although different shapes are possible.

Referring to FIG. 15, the variation of FIG. 15A may be extended to cover flat surfaces, with this bearing device having multiple rows 130 of multiple unobstructed regions 24 . In such embodiments, the bearing device prevents tilting about the X and Y axes while allowing relative motion in both the X and Y directions about the Z axis. The overall shape is shown as square or rectangular, but may be circular or have different shapes.

5, 6 and 7, a variation of the embodiment of FIGS. 4 and 5 is shown. In that variant, the active device 20 is arranged below the layer of material forming the first surface, similar to the variant of FIG. This provides a perfectly uniform (ie smooth) first surface, facilitating the manufacturing process. An additional advantage is that the bearing is less brittle and more resistant to wear and tear. In FIG. 6, the occlusive regions 22A, 22B, 22C and the non-occluded regions 24A, 24B, 24C are shown in dashed lines because they are not visible due to the active devices 20A, 20B and 20C being positioned below the first surface 12. ing.

Journal Bearings Referring to FIG. 8, another variant of the invention is shown, in which the bearing device is a journal bearing, also called radial bearing. Figure 8 shows the outer part of the journal bearing device. The inner part may be a shaft, not shown for clarity. The outer portion has an inner surface 12 defined as a first surface. The shaft has an outer surface forming a second surface. A bearing gap is defined between the inner surface 12 and the outer surface. The bearing device has a main axis of rotation 30 . The first surface 12 and the second surface are cylindrical and extend about a primary axis of rotation 30 .

In another embodiment, the bearing device may be conical, and in such variations the first and second surfaces are also conical.

The bearing device comprises a plurality, in particular five non-obstructing areas 24A, 24B, 24C, 24D, 24E. A number of 5 has the advantage that axial tilting about the radial axes Y, Z can be supported by independently controlling the pressure in the different non-occluded regions. Note that numbers other than 5 are also possible. Each non-occluded area is surrounded by an occluded area 22A, 22B, 22C, 22D, 22E.

Each occluded region has a first axial portion A1 and a second axial portion A2 extending a predetermined axial distance D1 and a first circumferential portion extending a predetermined circumferential distance D2. C1 and a second circumferential portion C2. Each occlusion region comprises four corners 32 interconnecting the first and second axial portions and the first and second circumferential portions. Although this is illustrated only for the occlusion area 22D, it is clear that the same is true for the other occlusion areas.

If the bearing device is conical, a similar configuration may apply, with the difference being that the occlusive and non-occluded areas are tapered.

In one embodiment, a control unit 101 may be provided and sensors 102 may be provided to sense axial tilt about the radial axes Y,Z. The control unit may be connected to a source of pressurized fluid or to a control valve in a conduit extending from the source of pressurized fluid to the inlet to individually control the pressure inside the non-occluded region. Additionally or alternatively, sensors may be provided to measure the position and/or orientation of the shaft with respect to the inner surface, and the control unit controls the individual unoccluded regions to control the position and/or orientation of the shaft with respect to the inner surface. It may be configured to control the pressure within.

Thrust Bearing Referring to Figure 9A, a thrust bearing device according to the present invention is illustrated. Thrust bearings are configured to carry loads in the axial direction and are sometimes referred to as axial bearings. Only one of the first surfaces 12 is shown.

The first surface 12 and the second surface are annular and extend about the main axis of rotation 30 of the bearing. A primary axis of rotation 30 extends orthogonally to the first surface 12 and the second surface.

Bearing device 10 includes an outer bearing end 26A and an inner bearing end 26B. The bearing device includes at least one outer active device 20A extending circumferentially and defining an outer closed region 22A, the outer active device 20A extending from at least one non-occluded region 24 to an outer peripheral bearing edge 26A. inhibit the flow of lubricant to

The bearing device includes at least one inner active device 20B extending circumferentially and defining an inner closed region 22B, the inner active device 20B extending from at least one non-occluded region 24 to an inner peripheral bearing edge. inhibit the flow of lubricant to 26B;

At least one non-occluded region 24 is annular and disposed between the inner occlusive region and the outer occlusive region.

The bearing device comprises a plurality of feed inlets 18 on the first surface 12 . This embodiment is a hydrostatic bearing device in which hydrostatic pressure creates the pressure necessary to carry the load and prevent contact between the first and second surfaces. . Circumferentially blocked areas 22A, 22B prevent lubricant from exiting the annular unblocked area through bearing gap ends 26A, 26B.

Thrust Bearing with Multiple Unobstructed Areas Referring to FIG. 9B, in another embodiment the thrust bearing device may have multiple unobstructed areas 24A, 24B, 24C, in particular three unobstructed areas, These non-occluded regions are circumferentially spaced about the main axis of rotation 30 . Each unobstructed area 24A, 24B, 24C has an inlet 18. As shown in FIG. Each occluded region is
- an inner peripheral section (33A) extending along part of the inner bearing gap edge;
- a peripheral section (33B) extending along part of the outer bearing gap edge;
- a first radial portion (29A) and a second radial portion (29B) extending over a predetermined radial distance (Dr) and interconnecting the inner and outer peripheral sections;
Prepare. In this embodiment, the non-obstructing area has an arcuate shape. This embodiment allows individual pressure control in different non-occluded regions 24 .

Hydrodynamic Bearing Referring to FIG. 10A, another embodiment is illustrated in which the bearing device is configured as a hydrodynamic bearing device. The bearing device has a first bearing surface 12 and a second bearing surface, although the second bearing surface is not shown in order to better show the first bearing surface 12 . The second bearing surface faces the first bearing surface. The first and second bearing surfaces are configured to rotate relative to each other about a primary axis of rotation 30 . The first and second bearing surfaces are flat and annular and extend perpendicular to the main axis of rotation 30 .

A bearing gap is defined between the first bearing surface and the second bearing surface. The first and second bearing surfaces are smooth and free of surface texturing. The bearing gap 16 is free of abrupt changes in the height of the bearing gap. The bearing gap is filled with a lubricant, the lubricant being a magnetorheological or electrorheological liquid or a lubricant with a temperature dependent viscosity.

A plurality of active devices 20 are embedded in the first (or second) bearing surface 12 and configured to locally increase the viscosity of the lubricant within the plurality of occlusion regions 22 . The effect of this is that lubricant flow through the bearing gap is blocked at each blockage area 22 .

The bearing device comprises a plurality of unobstructed areas 24 through which lubricant flow is unobstructed. Circumferentially alternating occlusive and non-occluded areas, each non-occluded area 24 being located between two occlusive areas 22 .

The effect of the blocked area is pronounced in the non-blocked area 24 upstream of the blocked area when considering the flow direction 34 (indicated by the arrow) of the lubricant relative to the blocked area 22 . For example, the effect of an occlusive region 22J is felt at a non-occluded region 24J located upstream of the occlusive region 22J.

Each occluded region is curved or angular in shape. Each occluded region extends over a predetermined radial distance Dr, which may be equal to the width W1 of the annular first or second surface.

For angular shapes, the herringbone pattern shown in FIG. 10A has been found to be advantageous. Herringbone patterns are known from hydrodynamic bearings with surface texturing in the form of grooves. In these bearings the herringbone pattern is created by surface texturing. This requires very precise machining. The resulting bearings are very sensitive to wear and tear. Damage to the surface texture as a result of contact between the first and second surfaces can easily cause malfunction of the bearing device. The present invention provides important advantages in this respect.

The curved or angular shape defines a downstream oriented apex 36 . The occlusive area is configured to prevent lubricant flow across each occlusive area by locally increasing viscosity within the occlusive area when the first and second surfaces move relative to each other. and particularly in the peak region 38 of each blocked region 24 located immediately upstream of each crest 36, to cause a local increase in lubricant pressure in the bearing gap. It is configured.

The curved or angular shape of the closed region 24 urges the lubricant radially toward the peak region, as indicated by arrows 40 in FIG. The left side 42 and right side 43 of the closed area 22 urge the lubricant towards the peak area. More specifically, the lubricant flow contracts somewhat in the peak region 38 resulting in a higher dynamic pressure of the lubricant in the peak region 38 . Obviously, a curved shape would work as well. In another embodiment, the top 36 may be open, resulting in a single left side 42 of component area and a single right side 43 of component area. The left and right sides may also be staggered. This is still considered an angular shape because the left side of the occluded area is tilted with respect to the right side and also with respect to the radial direction.

Each apex 36 is located in a central region of the first surface 12 and the apex 38 is particularly located a predetermined distance (A1) from the inner bearing end 26B, the distance (A1) being , between 30 and 70 percent of the width (W1) of the first surface 12 or the second surface, more specifically between 40 and 60 percent.

The occlusive region may have a V-shape (herringbone configuration) as shown in FIG. 10A, or it may have a U-shape.

Referring to FIG. 10B, a linear variation of hydrodynamic bearing device 10 is shown. The linear variation works much the same as the circular variation of FIG. 10A.

Referring to FIG. 11, occluded regions 22 defined by active devices 20 are spaced around the first or second surface and extend a predetermined axial distance (Da) in the direction of major axis 30 . An existing hydrodynamic journal bearing is shown. The occluded area is curved or angled. In the case of a curved shape, the curvature may be catenary, parabolic, generally U-shaped, or of different curvature. In the case of an angled shape, the occluded region may have a single angled apex (V shape), or it may have multiple angles, for example three angles (or corners), and one The central angle defines the top and left and right angles.

Referring to FIG. 12, another embodiment of the invention is shown, which is a hydrodynamic journal bearing device 10. As shown in FIG. The bearing device comprises a cylindrical bearing member 13 having a first surface 12 facing inwardly and extending around the shaft. The shaft has a second surface facing outward. The shaft is not shown in FIG. 12 in order to show the first surface 12 more clearly.

A hydrodynamic journal bearing device has a predetermined bearing length (L1). The bearing device has a bearing gap and has a first bearing gap end 26A and an opposite second bearing gap end 26B. The first bearing gap end 26A and the second bearing gap end 26B are located at opposing first and second bearing ends 40A, 40B.

A bearing gap exists between the first inwardly facing bearing surface and the second outwardly facing bearing surface. The first surface 12 and the second surface are smooth and continuous. The bearing gap is filled with lubricant. The lubricant is a magneto-rheological liquid, an electro-rheological liquid, or a lubricant with a temperature-dependent viscosity.

At least the first active device 20A and the second active device 20B are embedded in the first or second surface and the viscosity of the lubricant within the first and second closed regions 22A, 22B in the bearing gap is configured to locally increase The first and second active devices, when activated, increase the viscosity of the lubricant within the first and second occlusion areas to prevent the lubricant from flowing beyond the first and second occlusion areas. prevent

The first surface 12 and the second surface are smooth and continuous without surface texturing in the form of ridges and pads, without abrupt changes in bearing gap height. The bearing gap comprises at least one unobstructed area 24 through which lubricant flow is unobstructed.

The first and second bearing gap ends 26A, 26B are annular and extend around the shaft and in a plane perpendicular to the longitudinal bearing axis 30. As shown in FIG.

The first and second closure regions 22A, 22B are ring-shaped and located at opposite ends 40A, 40B of the journal bearing. A non-occlusive region 24 is positioned between the first occlusive region 22A and the second occlusive region 22B.

The first blocked area 22A prevents lubricant from reaching the first bearing gap end 26A and the second blocked area 22B prevents lubricant from reaching the second bearing gap end 26B. prevent Together, the first blocked area 22A and the second blocked area 22B prevent lubricant from flowing out of the non-blocking area 24 and out of the bearing gap through the bearing gap ends 26A, 26B.

As with most hydrodynamic journal bearings, the height of the bearing gap may vary circumferentially. When the axis is aligned with the cylindrical bearing member 13, the height of the bearing gap is constant in the axial direction. In practice, however, small deviations may occur as a result of loads on the axis.

The bearing has a length L1 and each occlusion area has a width Woz. The width Woz of each occlusion region is less than 10 percent of the bearing length L1. This results in an unobstructed region 24 forming at least 80 percent of the length of the bearing.

Referring to Figure 13A, a drive assembly 100 comprising a shaft 50 is shown supported by at least one bearing device 10, in particular three bearing devices 10 according to the invention.

The shaft is supported by a first journal bearing device 10A and a second journal bearing device 10B and a third thrust bearing device 10C providing support in the axial direction X, the first and second bearing devices are journal bearing devices and provide support in radial directions Y, Z;

Drive assemblies may be used in a variety of applications.

Referring to FIG. 13B, in one application, drive assembly 100 is used on board a watercraft 104, which includes hull 106, engine 108, propeller 110, and drive assembly 100 connecting the engine to the propeller.

The shaft is supported by a first journal bearing device 10A and a second journal bearing device 10B and by a third thrust bearing device providing support in the axial direction X, the first and second journal bearings The device provides support in two independent radial directions Y, Z.

The engine further comprises gearbox 112 , outboard seal 114 and inboard seal 115 . Seals 114 , 115 prevent ingress of seawater 116 . The engine 108 and gearbox 112 are located within an engine room 118 and may be separated from the rest of the vessel's interior volume by one or more bullheads 120 . Shaft 50 is generally disposed within stern tube 122 . The annular space 124 between the stern tube 122 and the shaft 50 may be filled with oil.

Further Embodiments Referring to Figures 16 and 17, another embodiment is shown. One or more active devices 20 are referred to as primary active devices. The bearing device further comprises one or more reactive devices 44, which may be electromagnets or permanent magnets or electroactive devices or heating elements. The counteractive device is used to counteract the magnetic or electric field created by the primary active device 20 in at least a portion of the non-occluded region 24 or to heat the lubricant in or in at least a portion of the non-occluded region. creates a magnetic or electric field in the opposite direction.

In this embodiment, primary active device 20 is a coil extending around inlet 18 . The coil has a main axis 30 . The deactivator 44 is also a coil extending around the inlet 18 and having the same main axis 30 . When viewed in the X direction (extending parallel to the coil axis 30), the primary activator 20 and the deactivator 44 form concentric circles.

The counter-actuator 44 acts on a portion of the non-occluded area, which is referred to as the anti-occluded area 46 . The non-occluded regions 24 further include a non-affected region 48 not under the influence of the primary active device or the counter-active device, and at least one anti-occlusion region is adjacent to the occlusion region and separates the occlusion region and the non-affected region. is placed between

Active device 20 is an electromagnet. The bearing device further comprises at least one passive ferromagnetic member 60 configured to increase the electromagnetic field.

Coils 20 , 44 are positioned below first surface 12 and below material layer 28 . The ends 62 of the coil are positioned a predetermined distance (Dc) from the first surface 12 and the coil is positioned below the first surface 12 . The at least one ferromagnetic member comprises an inner member 64 located within the coil and an outer member 66 located outside the coil. Inner member 64 and outer member 66 each have an inner projection 65 and an outer projection 67 extending beyond coil end 62 toward first surface 12, and opening 70 defines the inner and outer projections. provided between The area of bearing gap 16 above opening 70 is closed area 22 . At least one occluded region 22 completely surrounds at least one non-occluded region 24 .

Embodiments with Blocked Regions Within Non-Occluded Regions Referring to Figures 18, 19 and 20, there is shown an embodiment of a hydrostatic bearing device according to the present invention having a non-occluded region 24 surrounding an inner blocked region 22M. ing. The unoccluded region 24 is also surrounded by an outer annular occlusive region 22 .

The inner closed region 22M has the beneficial effect of damping vibrations (or resonances) that may occur in the two bearing surfaces that move relative to each other in a direction perpendicular to the first surface 12 . When the bearing surfaces move towards each other, a so-called "squeeze flow" is created. Squeeze flow is the flow of lubricant from the inner closed area 22M to the non-closed area 24 and from the non-closed area 24 through the closed area 22 to the bearing gap end 26 and out of the bearing gap.

Squeeze flow per se is well known in the field of bearing devices. However, in this embodiment, the lubricant in the bearing gap at central closed region 22M has increased viscosity (or increased slip angle). As a result, squeeze flow is impeded and less lubricant is squeezed out of the bearing gap. This results in better damping of vibrations or resonances.

Referring to Figures 21, 22 and 23, an embodiment of a hydrodynamic bearing device comprising a tilt pad 80 is shown. Bearing devices with tilting pads are known. The tilt pad is connected to the outer portion of the bearing device via a hinge 82 defining a pivot axis 84 . It is conceivable that the tilt pad is pivotable about two pivot axes extending at right angles to each other, for example via a spherical hinge.

In this embodiment, the direction of lubricant flow relative to the first surface 12 is indicated by arrows 34 . The shape of the occluded area 22 is the same as described with respect to the embodiment of Figures 10A, 10B and 11, with the difference that the tilt pad is generally square or rectangular. The obturating area 22 of the tilt pad may have a U-shape. The U-shaped closure area extends along three sides 88 of the tilt pad. The occluded region may have an angular form, such as a V-shape, or may have a curved form. Also, a single tilt pad may be provided with a plurality of occlusion areas side by side.

Arrow 34 not only indicates the direction of lubricant flow relative to the first surface, but also the direction of movement of the second surface relative to the first surface.

The occluded region 22 has a U-shaped "bottom" top 36 . Immediately upstream of the apex 36, a peak region 38 is formed in the non-occluded region. In peak region 38, the lubricant pressure reaches a maximum value.

Although only one tilt pad 80 is shown, it will be apparent that in a completed bearing device there will be multiple tilt pads spaced about the axis of rotation. For example, 3, 4, 6, or 8 tilt pads may be provided, although different numbers are possible. The first surface 12 of the tilt pad may be flat, but it may also be curved, as is known for tilt pads, or in particular concave.

In the case of a thrust bearing, the tilt pad may have the shape of a ring-shaped portion. These tilt pads together form a ring shape.

Those skilled in the art will appreciate that there is generally a non-supported area (ie, a non-supported gap) between two adjacent tilt pads. For the purposes of this specification, these unsupported areas are not considered part of the bearing gap. The characteristic uniformity of the first and second surfaces applies to separate first surface sections of the tilt pad. The features "no surface texturing" and "no abrupt changes in bearing gap height" also apply to the individual sections formed by the tilt pads.

The tilt pad need not be exactly square or rectangular. A trapezoidal shape is also possible. The tilt pad 80 may have rounded corners.

As required, detailed embodiments of the present invention are disclosed herein. However, it should be understood that the disclosed embodiments are merely exemplary of the invention, which may be embodied in various forms. Therefore, specific structural and functional details disclosed herein are not to be construed as limitations, but merely as a basis for the claims and the present invention to virtually any suitable detailed description. It should be construed as a representative basis for teaching those skilled in the art to use the various constructions. Moreover, the terms and expressions used herein are not intended to be limiting, but rather to provide an understandable description of the invention.

The terms "a" or "an," as used herein, are defined as one or more. The term "plurality", as used herein, is defined as two or more. The term "another", as used herein, is defined as at least a second and subsequent. The terms "including" and/or "having," as used herein, are defined as comprising (ie, open language that does not exclude other elements or steps). Any reference signs in the claims shall not be construed as limiting the scope of the claims or the invention.

The mere fact that certain measures are recited in mutually different dependent claims does not indicate that a combination of these measures cannot be used to advantage.

10 Bearing Device 12 First Surface 12A, 12B, 12C First Surface Section 14 Second Surface 16 Bearing Gap 18 Feed Inlet 20 Active Device 22, 22A, 22B, 22C, 22D, 22E Closure Area 24, 24A, 24B , 24C, 24D, 24E unblocked area 25 flow path 26 bearing gap end 26A outer bearing edge 26B inner bearing edge 28 material layer 30 main axis of rotation 32 corner 36 apex 38 peak area 40 second bearing edge 42 left section 43 right section 44 counter-activation device 46 anti-occlusion region 48 non-affected region 50 shaft 60 ferromagnetic member 62 end of coil 64 inner member 65 inner protrusion 66 outer member 67 outer protrusion 70 aperture 80 tilt pad 100 drive assembly 101 Control Unit 102 Sensor 104 Vessel 106 Hull 108 Engine 110 Propeller 112 Gearbox 114 Outboard Seal 114 Seal 115 Inboard Seal 115 Seal

Claims (42)

A bearing device (10) comprising:
- a first surface (12) and a second surface (14) movable relative to each other and facing each other, said first surface and said second surface being filled with a lubricant; A first surface separated by a bearing gap (16) and wherein the lubricant is a magnetorheological or electrorheological liquid, a lubricant with a temperature dependent viscosity, or a lubricant with a controllable slip velocity. and a second surface;
- one or more feed inlets (18) in said first surface or said second surface, each of said feed inlets directing said lubricant from a pressurized liquid supply to said bearing gap (16); a feed inlet configured to feed;
- one or more active devices (20) embedded in said first surface or said second surface to localize the viscosity of said lubricant within at least one closed area (22) in said bearing gap; configured to globally increase or locally reduce the slip velocity of the lubricant, thereby locally blocking flow of the lubricant through the bearing gap within the blockage region. an active device;
and
said bearing gap comprising at least one unobstructed area (24) in which said lubricant flow is unimpeded, each said unobstructed area surrounding said associated feed inlet (18);
A flow path for said lubricant through said bearing gap is defined, said flow path beginning at said at least one feed inlet (18) and extending along said at least one unobstructed area (24). , traverses the closure area and terminates at a bearing gap end (26);
Said first surface (12) and said second surface (14) are free of surface texturing, particularly in the form of ridges and pads, smooth and continuous, and are free from abrupt changes in the height of said bearing gap. without significant changes
at least one said occlusive region (22) by itself or in cooperation with other occlusive regions surrounds at least one said non-occluded region (24);
The lubricant with increased viscosity or reduced slip velocity at the clogged area acts as a blockage in the flow path and has increased viscosity or slip velocity by itself or at other clogged areas. cooperates with the reduced lubricant to prevent said lubricant from flowing out of said non-blocking area and out of said bearing gap through said bearing gap end, thereby increasing the pressure of the lubricant within the occlusion area to a level sufficient to carry the load on the bearing device while preventing contact between the first surface and the second surface; A bearing device characterized by: Said active device (20) is an electromagnet or permanent magnet that creates a magnetic field, or an electro-active device that can be charged to create an electric field, or said active device comprises said lubricant in at least one of said occlusion regions. 2. A bearing device according to claim 1, characterized in that it is a cooling element arranged to cool the comprising a plurality of unobstructed areas (24A, 24B, 24C), in particular three unobstructed areas and a plurality of obstructed areas (22A, 22B, 22C) each having a respective said feed inlet (18); ,
1 or claim 2, wherein each of said occlusion areas surrounds said non-occlusion area associated with said occlusion area and prevents said lubricant from escaping said associated non-occlusion area. 2. The bearing device according to 2. 4. Any of claims 1 to 3, wherein the non-occluded area is pie-shaped, circular, square, rectangular, triangular, polygonal, e.g. hexagonal, elliptical, or a combination of these shapes. or a bearing device according to claim 1. from claim 1, characterized in that said first surface (12) and said second surface (14) are cylindrical or conical and extend about a principal axis of rotation (30) 5. A bearing device according to any one of claims 4. the first surface and the second surface are cylindrical or conical;
The bearing device comprises a plurality of non-occluded areas (24A, 24B, 24C, 24D, 24E) each surrounded by an occlusive area (22A, 22B, 22C, 22D, 22E). and
Each of said closed regions has a first axial portion (A1) and a second axial portion (A2) extending over a predetermined axial distance (D1) and a a first circumferential portion (C1) and a second circumferential portion (C2) extending;
Each of said closed areas has four corners interconnecting said first and second axial portions and said first and second circumferential portions ( 32). comprising at least a ring-shaped first occlusion area (22A) and a ring-shaped second occlusion area (22B);
said first closed area (22A) is located at a first end (40A) of a cylindrical or conical bearing;
said second closed area (22B) is located at the opposite second end (40B) of said cylindrical or conical bearing;
The non-occlusive area is provided between the first occlusive area and the second occlusive area,
The first closed area and the second closed area act as seals to prevent the lubricant from exiting the non-closed area and out of the cylindrical or conical bearing gap through the bearing gap end. 6. A bearing device according to claim 5, characterized in that: A bearing device according to any one of claims 1 to 7, characterized in that said first surface (12) and said second surface (14) are spherical. A bearing device according to any one of claims 1 to 4, characterized in that said first surface (12) and said second surface (14) are flat. A thrust bearing configured to carry an axial load,
said first surface and said second surface being annular and extending about a main axis of rotation (30) of said bearing device;
Said main axis of rotation (30) extends perpendicular to said first surface and said second surface and said bearing device comprises an outer bearing end (26A) and an inner bearing end (26B). ), said bearing device comprising at least one outer closed area (22A) for blocking the flow of said lubricant from said at least one unclosed area to said peripheral bearing end (26A); at least one inner obstructed area (22B) that prevents the flow of said lubricant from said one unobstructed area to said inner peripheral bearing end (26B);
10. A bearing device according to claim 9, characterized in that at least one non-blocking region (24) is arranged between the inner blocking region and the outer blocking region. Said first surface and said second surface are flat or spherical and said bearing device comprises an outer bearing gap end (26) and said lubricant flows from said bearing gap through said outer bearing gap end. 1, 2, 4, 8 or claim 1, 2, 4, 8 or claim 1, characterized in that it comprises an unobstructed area (24) surrounded by an annular obturated area (22) preventing outflow. 9. The bearing device according to 9. 12. A bearing device according to any one of the preceding claims, comprising at least one outer closure region surrounding an inner closure region. one or more of said active devices (20) are referred to as primary active devices,
The bearing device further comprises one or more reactive devices (44), which may be electromagnets or permanent magnets or electroactive devices or heating elements,
The counter-active device creates a counter-magnetic or counter-electric field to counteract the magnetic or electric field produced by the primary active device in at least a portion of the non-occluded region, or 13. A bearing device according to any one of the preceding claims, characterized in that it is a heating element for heating the lubricant at least in part. said counteractive device (44) acts on a portion of said non-occluded area;
This portion is called an anti-occlusion area,
said non-occluded region further comprising a non-affected region (48) not under the influence of said primary active device or said counter-active device;
14. Bearing according to claim 13, characterized in that at least one anti-obstruction area (46) is arranged adjacent to the obturator area (24) between the obturator area and the non-affected area. device. 15. The apparatus of claims 1-14, wherein the active device is an electromagnet and the bearing device further comprises at least one passive ferromagnetic member (60) configured to increase the electromagnetic field. A bearing device according to any one of the preceding clauses. The electromagnetically active device is a coil having a primary axis of rotation (30), said coil being disposed below said first surface (12) or said second surface (14), the ends of said coil a portion (62) is positioned at a predetermined distance (Dc) from said surface under which said coil is positioned;
the at least one ferromagnetic member comprises an inner member (64) positioned inside the coil and an outer member (66) positioned outside the coil;
The inner and outer members each comprise an inner projection (65) and an outer projection (67) extending beyond the ends of the coil towards the first surface or the second surface. cage,
16. Bearing device according to claim 15, characterized in that an opening (70) is provided between the inner projection and the outer projection. 17. A bearing device according to any one of the preceding claims, characterized in that the bearing device is free of roller elements, such as ball or cylindrical roller elements. One or more of said active devices are characterized in that they are located under a layer (28) of material covering at least one of said active devices and forming said first surface or said second surface. 18. A bearing device according to any one of claims 1-17. 19. A bearing device as claimed in any one of the preceding claims, wherein the closed area is defined by a plurality of the active devices arranged adjacent to each other along a predetermined line. 20. A bearing device according to any preceding claim, wherein the bearing gap has a uniform height between the feed inlet and the bearing gap end. A hydrodynamic bearing device (10) comprising:
- a first bearing surface (12);
- a second bearing surface (14) facing said first bearing surface (12);
and
said first bearing surface and said second bearing surface are configured to rotate relative to each other about a primary axis of rotation (30);
The hydrodynamic bearing device is
- a bearing gap (16) defined between said first bearing surface and said second bearing surface, said first bearing surface and said second bearing surface being smooth and surfaces; There is no texturing, the bearing gap is free of abrupt changes in height of the bearing gap, and the bearing gap is filled with a lubricant, the lubricant being a magneto-rheological liquid or an electro-rheological liquid. , a lubricant with a temperature dependent viscosity or a lubricant with a controllable slip velocity, the bearing gap (16);
- a plurality of active devices (20) embedded in said first bearing surface or said second bearing surface for locally increasing the viscosity of said lubricant in a plurality of occlusion areas (22); or a plurality of active devices configured to locally reduce the slip velocity, thereby inhibiting flow of the lubricant through the bearing gap at each of the blockage areas;
- a plurality of unobstructed areas (24) in which the flow of said lubricant is not impeded, said obstructed areas and said unobstructed areas in the direction of relative movement between said first bearing surface and said second bearing surface; a plurality of non-occluded regions, alternating regions, each of said non-occluded regions positioned upstream of the associated occlusive region;
and
each of the occluded regions has a curved shape or an angular shape;
said curved or angled shape defines a downstream oriented apex (36);
The occlusion area locally increases the viscosity or locally decreases the slip velocity at the occlusion area as the first bearing surface and the second bearing surface move relative to each other. by blocking the flow of said lubricant across each of said blocked areas by means of a A hydrodynamic bearing device, characterized in that it is arranged to cause a local increase in pressure of said lubricant in said bearing gap in a peak region (38). Each of said closed areas comprises a left section (42) and a right section (40) extending at an angle to the radial direction, said left section and said right section directing said lubricant to said peak. 22. A hydrodynamic bearing device according to claim 21, characterized in that it is oriented towards the area (38). each of the apexes is located in a central region of the first bearing surface or the second bearing surface;
said apex (36) is in particular arranged at a predetermined distance (A1) from an inner bearing end (26B) of said first bearing surface or said second bearing surface,
Claim characterized in that said distance (A1) is between 30% and 70%, more particularly between 40% and 60% of the width (W1) of said first bearing surface or said second bearing surface. 23. A hydrodynamic bearing device according to claim 21 or claim 22. is a thrust bearing device,
the first bearing surface and the second bearing surface are flat and extend perpendicular to the primary axis of rotation;
24. A hydrodynamic bearing device according to any one of claims 21 to 23, wherein said closed area extends over a predetermined radial distance (Dr). 25. A hydrodynamic bearing according to any one of claims 21 to 24, wherein said first bearing surface and said second bearing surface are annular and said bearing gap is annular. device. 26. A hydrodynamic bearing device according to any one of claims 21 to 25, characterized in that said closed area (22) has a V-shape or a U-shape. said hydrodynamic bearing device being a tilting pad bearing device and comprising a plurality of tiltable tilting pads (80);
Said first bearing surface (12) comprises a plurality of first surface sections (12A, 12B, 12C), each of said first surface sections (12A, 12B, 12C) being associated with a tilt pad. is associated with
said bearing gap comprising a plurality of bearing gap sections, each of said bearing gap sections being associated with a tilt pad;
Each of said first surface sections is smooth and free of surface texturing, and each of said bearing gap sections between a tilt pad and said opposite second bearing surface includes said bearing gap (16 ) without sudden changes in the height of
each of said first surface sections comprising an occluded area (22) having a curved or angular shape;
said curved or angular shape defines a downstream oriented apex (36);
The occlusion area locally increases the viscosity or locally decreases the slip velocity at the occlusion area as the first bearing surface and the second bearing surface move relative to each other. by blocking the flow of said lubricant across each of said blocked areas by means of a 27. The lubricant according to any one of claims 21 to 26, characterized in that it is arranged to cause a local increase in the pressure of the lubricant in the bearing gap in a peak region (38) which is rounded. hydrodynamic bearing device. The bearings are journal bearings or conical bearings,
said curved or angled occlusive regions are spaced around said first bearing surface or said second bearing surface and extend a predetermined axial distance (Da); 28. A hydrodynamic bearing device according to any one of claims 21-23 and 25-27, characterized in that A hydrodynamic journal bearing device comprising:
- a cylindrical bearing member (13) extending around the shaft, the cylindrical bearing member (13) comprising a first surface (12) facing inwardly;
- a shaft (50) comprising a second surface (14) facing outwards;
and
The hydrodynamic journal bearing device has a predetermined bearing length (L1) and has a first bearing end (40A) and an opposite second bearing end (40B). cage,
The hydrodynamic journal bearing device is
- a bearing gap (16) present between said first surface (12) and said second surface (14), said bearing gap being the first bearing at said first bearing end; said first surface (12) and said second surface (14) having a gap end (26A) and a second bearing gap end (26B) at said second bearing end, said first surface (12) and said second surface (14) being smooth; and continuous, the bearing gap being filled with a lubricant, the lubricant being a magnetorheological or electrorheological liquid, a lubricant with a temperature dependent viscosity, or a controllable slip velocity a bearing gap, a lubricant comprising
- at least a first active device (20A) and a second active device (20B) embedded in said first surface or said second surface, wherein said first closed area (22A) in said bearing gap; and a second occlusion area (22B) configured to locally increase the viscosity of said lubricant or locally decrease said slip velocity, wherein said first active device and said second active device; The device, when activated, increases the viscosity of the lubricant or decreases the slip velocity in the first and second occlusion areas such that the lubricant is in the first occlusion area. and a first active device and a second active device that prevent outflow across said second occlusive region;
and
said first surface (12) and said second surface (14) are smooth and continuous without surface texturing, without abrupt changes in height of said bearing gap;
said bearing gap comprises at least one non-obstructed area (24) where flow of said lubricant is not impeded;
The first bearing gap end and the second bearing gap end are annular and extend around the shaft and extend in a plane orthogonal to the longitudinal bearing axis (30). and
The first closed area and the second closed area are ring-shaped and at the first bearing end (40A) and the second bearing end (40B) of the hydrodynamic journal bearing device. and wherein the non-occluded region is disposed between the first occlusive region and the second occlusive region;
The first blockage area prevents the lubricant from reaching the first bearing gap end and the second blockage area prevents the lubricant from reaching the second bearing gap end. prevent it from reaching
Both the first closed area and the second closed area allow the lubricant to flow out of the non-closed area and through the first bearing gap end and the second bearing gap end. A hydrodynamic journal bearing device, characterized in that it prevents outflow from a bearing gap. 30. The hydrodynamic journal bearing device of claim 29, wherein the height of said bearing gap varies in the circumferential direction. 31. A hydrodynamic journal bearing device according to claim 29 or 30, wherein the height of the bearing gap is constant in the axial direction. The hydrodynamic journal bearing device has a predetermined length (L1),
Each of the first occlusion area and the second occlusion area has a predetermined width (Woz),
32. Any of claims 29 to 31, wherein the width (Woz) of each of the first occlusion area and the second occlusion area is less than ten percent of the length (Ll). or the hydrodynamic journal bearing device according to claim 1. A drive assembly (100) comprising a shaft (50), comprising:
33. A drive assembly, wherein the shaft is supported by at least one bearing device according to any one of claims 1-32. The shaft comprises a first bearing device (10A) according to any one of claims 1 to 32 as far as journal bearing devices are concerned and any one of claims 1 to 32 as far as journal bearing devices are concerned. supported by a second bearing device (10B) according to one claim and a third bearing device (10C) according to any one of claims 1 to 32 as far as thrust bearing devices are concerned cage,
a first journal bearing device and a second journal bearing device position and provide support for the shaft in two independent radial directions (Y, Z);
34. Drive assembly according to claim 33, wherein a third thrust bearing device positions and provides support for the shaft in the axial direction (X). 35. A marine vessel comprising a hull (106), an engine (108), a propeller (110) and a drive assembly according to claim 33 or 34 connecting said engine to said propeller. A hydrodynamic bearing device (10) comprising:
- a first bearing surface (12);
- a second bearing surface (14) facing said first bearing surface (12);
and
said first bearing surface (12) and said second bearing surface (14) are configured to rotate relative to each other about a primary axis of rotation (30);
The hydrodynamic bearing device is
- a bearing gap (16) defined between said first bearing surface and said second bearing surface, said bearing gap being filled with a lubricant, said lubricant being magnetically a bearing gap that is a viscous or electro-viscous liquid, a lubricant with a temperature dependent viscosity, or a lubricant with a controllable slip velocity;
- a plurality of active devices (20) embedded in said first bearing surface or said second bearing surface for locally increasing the viscosity of said lubricant in a plurality of occlusion areas (22); or a plurality of active devices configured to locally reduce the slip velocity, thereby inhibiting flow of the lubricant through the bearing gap in each of the blockage areas (22);
- a plurality of unobstructed areas (24) in which the flow of said lubricant is not impeded, said obstructed areas and said unobstructed areas in the direction of relative movement between said first bearing surface and said second bearing surface; a plurality of non-occluded regions, alternating regions, each of said non-occluded regions positioned upstream of the associated occlusive region;
and
Each of said occlusion regions has a curved or angled shape, said curved or angled shape defining a downstream oriented apex (36), said occlusion region locally increases the viscosity or locally decreases the slip velocity in the occlusion region to close the occlusion when the first bearing surface and the second bearing surface move relative to each other. A peak located in said non-occluded area located upstream of each of said closed areas and in particular immediately upstream of each of said crests (36) by blocking the flow of said lubricant across each of said areas. configured to cause a localized increase in pressure of the lubricant within the bearing gap in a region (38);
Said hydrodynamic bearing device is a tilting pad bearing device and comprises a plurality of tiltable tilting pads (80), said first bearing surface (12) comprising a plurality of first surface sections (12A , 12B, 12C), each of said first surface sections being associated with a tilt pad, said bearing gap comprising a plurality of bearing gap sections, each of said bearing gap sections being associated with a tilt pad is associated with
Each of the first surface sections is smooth and free of surface texturing, and each of the bearing gap sections between the tilt pad and the opposite second bearing surface has a height of the bearing gap. without abrupt changes
Each of said first surface sections comprises an occluded area (22) having a curved or angled shape, said curved or angled shape having a downstream directed apex (36). ), the occlusion area locally increasing the viscosity in the occlusion area or locally the By reducing the slip velocity and preventing the flow of the lubricant across each of the blocked regions, the non-blocked regions (24) located upstream of each of the blocked regions, and particularly the apex (36). ) is configured to cause a local increase in pressure of said lubricant in said bearing gap (16) in a peak region (38) located immediately upstream of each of said bearing gaps (16). device. each of said occlusion regions comprising a left section (42) and a right section (40) extending at an angle to the radial direction;
37. A hydrodynamic bearing device according to claim 36, wherein said left section and said right section direct said lubricant towards said peak region (38). each of the apexes is located in a central region of the first bearing surface or the second bearing surface;
said apex (36) is in particular located at a predetermined distance (A1) from an inner bearing edge (26B) of said first bearing surface or said second bearing surface,
Claim characterized in that said distance (A1) is between 30% and 70%, more particularly between 40% and 60% of the width (W1) of said first bearing surface or said second bearing surface. 38. A hydrodynamic bearing device according to claim 36 or claim 37. is a thrust bearing device,
said first bearing surface and said second bearing surface being flat and extending perpendicular to said main axis of rotation;
39. A hydrodynamic bearing device according to any one of claims 36 to 38, wherein said closed area extends over a predetermined radial distance (Dr). the first bearing surface and the second bearing surface are annular;
40. A hydrodynamic bearing device according to any one of claims 36 to 39, wherein said bearing gap is annular. 41. The hydrodynamic bearing device according to any one of claims 36 to 40, characterized in that said closed area (22) has a V-shape or a U-shape. The bearings are journal bearings or conical bearings,
The curved or angled occlusion areas (22) are spaced around the first bearing surface or the second bearing surface and extend a predetermined axial distance (Da). 42. A hydrodynamic bearing device according to any one of claims 36-38, 40 and 41, characterized in that

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